Note : Les descriptions sont présentées dans la langue officielle dans laquelle elles ont été soumises.
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WO96/19677 PCT~S9SJ16101
CLAMP SCREW
Detailed DescriPtion
Field of Industrial Use
This invention is used as a clamp screw (for
example a nut) for clamping a rotating tool such
as, for example, the grindstone of a hand-grinder,
or a circular hand-saw, to a threaded attachment
part (for example a male thread) provided on the
drive shaft of an electric tool.
Prior Art
When attaching a rotating tool such as said
grindstone or circular saw to the drive shaft of an
electric tool, in conventional practice a flange
and a male thread are formed at the end of the
drive shaft, the rotating tool is inserted over
this male thread, and a clamp screw formed with a
female thread, for example a nut, is screwed on
outside of this, this nut then being clamped using
a tightening tool such as a wrench.
Since said electric tool is a manual type
(portable), when using a wrench for clamping as
described above, the alignment of the electric tool
is unbalanced, and its work performance
deteriorates. Thus if the above-mentioned clamping
nut can be attached by rotation using a manual
operation only, work performance will be greatly
improved. Moreover, clamping using reverse thrust
from the use of the rotating tool will be even more
effective. However, when the nut is rotated in a
manual operation, a loss in clamping force occurs
due to the frictional resistance in the thread
portion of said male thread and the female thread
of the nut, with the difficulty that it is not
possible to create a sufficient clamping force
using the force of a manual operation alone.
Moreover, there is the disadvantage that if the
reverse thrust of the rotating tool is used without
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being checked, too much clamping may occur so that
it cannot be removed.
Problems To Be Resolved By The Invention
This invention has as its purpose the
provision of a clamp screw in which the loss of
clamping force is greatly reduced, a powerful
clamping force can be obtained with a small
rotational input, a sufficient clamping force can
be obtained by a manual operation, and moreover, a
sufficient clamping force can be obtained without
excessive clamping by making effective use of the
reverse thrust of the rotating tool.
Means of Resolving the Problems
The invention of Claim l of the invention is
characterised by being a clamp screw which is
provided with a threaded member with a threaded
part having a female or male thread formed on a
shaft part and which screws onto a threaded
attachment part, and with a shaft-shaped peripheral
part formed on its outer surface, an operating ring
whose inner part is inserted over the shaft-shaped
peripheral part of said threaded member, and to
which a rotational force is input externally, and a
flange ring fitted facing said op~erating ring so as
to freely rotate on said shaft-shaped peripheral
part of said threaded member and permitted a slight
movement in the axial direction, and in contact
with the attached object, thread grooves of the
same respective thread pitch being engraved into
the inserted and engaged inner and outer surfaces
of said threaded member and operating ring, a
plurality of balls being fitted into said thread
grooves, a restraining ring being installed between
said operating ring and flange ring with slight
freedom of movement in the axial direction with
respect to the threaded member but prevented from
rotating, a spring means being fitted between said
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restraining ring and operating ring, which returns
said operating ring to its initial position
allowing for the set number of turns in the
clamping range, and a dry metal being fitted
between said restraining ring and flange ring in
contact with both of these and applying the
required frictional resistance.
The invention of Claim 2 of the invention, in
addition to the structure of the invention of Claim
1, is characterised by being a clamp screw in which
a thrust bearing is fitted between said operating
ring and restraining ring.
The invention of Claim 3 of the invention, in
addition to the structure of the invention of Claim
1, is characterised by being a clamp screw in which
said balls, in addition to being retained by a
ret~in;ng ring fitted between the respective thread
grooves of the threaded member and the operating
ring, are arranged at a mutual distance with
adjacent balls in the direction of the thread pitch
having their positions spaced along the direction
of thread pitch.
The invention of Claim 4 of the invention, in
addition to the structure of the invention of Claim
1, is characterised by being a clamp screw in which
a thrust bearing is fitted between said operating
ring and restraining ring, an adjustment ring is
fitted between said thrust bearing and restraining
ring, raised parts being formed on one of the
circumferences of the respectively opposing
surfaces of said adjustment ring and operating
ring, contact parts which are able to slip and are
sprung against said raised parts being formed on
the other.
With the clamp screw of Claim 1 of the
invention, when the operating ring is rotated with
the threaded part of the threaded member screwed
- -
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onto the threaded attachment part, until the flange
ring comes into contact with the object being
attached it rotates in the same way as a single
threaded member, as it forms a unit through the
assembled resistance of the structural elements.
Then when the flange ring comes in contact with the
object being attached, the rotation of the threaded
member stops and it enters the clamping state, the
rotation of the operating ring is screw fed due to
the balls moving around the thread grooves, and due
to this screw feed the movement of the operating
ring creates a pressure against the flange ring
through the restraining ring, so that this pressure
produces a clamping force on the object being
attached. Moreover, the rotation of said operating
ring during the screw feed of said operating ring
has virtually no frictional resistance due to the
movement of the balls around the thread grooves, so
that the rotative force of the operating ring can
be applied to the flange ring effectively with no
loss.
When the object to be attached is fixed as
described above, and this attached object is used,
the reverse thrust due to the resistance to this
use is transmitted to the flange ring, rotating
this in the direction of clamping. This reverse
rotation is transmitted to the restraining ring
through said dry metal until the dry metal slips,
and a relative rotation in the direction of
clamping is generated between this restraining ring
and the operating ring, the mutual clamping force
is increased, and due to this increased clamping
force (extra clamping) a more effective clamping is
obtained.
However, when the reverse rotation is greater
than the level at which the coefficient of friction
of the dry metal has been set, slippage occurs
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between this dry metal and the flange ring, thus
preventing over-clamping.
When removing the clamp screw, by rotating the
operating ring in the opposite direction to the
above, the pressure from the said operating ring on
the flange ring is released, and the clamping can
be loosened, and thereafter it can be removed like
a single threaded member. Also there is no loss of
rotative power when the operating ring is turned in
reverse when loosening it as described above, since
the balls move around the thread grooves.
Furthermore, when the load is removed from the
operating ring on the flange ring side, the
operating ring returns to its initial position with
respect to the threaded member due to the spring
means.
With the clamp screw of Claim 2 of the
invention, in addition to the effect of the
invention of said Claim 1, there is virtually no
frictional resistance between the operating ring
and the restraining ring, so that the rotational
force of the operating ring can be transmitted to
the flange ring effectively and without loss.
With the clamp screw of Claim 3 of the
invention, in addition to the effect of the
invention of said Claim 1, the position of the
balls is maintained by the retaining ring, ensuring
the balls have a smooth turning movement.
With the clamp screw of Claim 4 of the
invention, in addition to the effect of the
invention of Claim 1, when the operating ring
enters the clamping state, the adjustment ring also
receives the pressure between the operating ring
and stops rotating, and due to its stopping a
relative rotation takes place between the operating
ring and the adjustment ring, and adjustment and an
adjustment noise is generated by slippage between
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the raised parts and the contact part, and the
clamping state can be verified by this adjustment
and adjustment noise.
According to the invention of Claim 1 of the
invention, when the flange ring comes into contact
with an attached tool, the rotation of the threaded
member stops and it enters a clamping state, the
rotation of said operating ring during screw feed
of the operating ring has virtually no frictional
resistance due to the movement of the balls around
the thread grooves, so the rotational force of the
operating ring can be transmitted effectively and
without loss to the flange ring, it is possible to
fix the clamp strongly even with a small rotational
force, and manual operation can be made to exert a
sufficient clamping force.
Moreover, as the dry metal is fitted, a more
effective clamping is obtained due to the increased
clamping force (extra clamping) resulting from the
reverse rotation of the attached object.
In addition, when the reverse rotation is
greater than the level at which the coefficient of
friction of the dry metal has been set, slippage
occurs between this dry metal and the flange ring,
thus preventing over-clamping.
According to the invention of Claim 2 of the
invention, in addition to the effect of the
invention of said Claim 1, since there is virtually
no frictional resistance between the operating ring
and the restraining ring during said clamping state
because of the thrust bearing, there is no loss in
rotational force in said part, and a small
operating force such as a hand movement can be made
more efficiently and effectively to have sufficient
effect as a clamping force.
According to the invention of Claim 3 of the
invention, in addition to the effect of the
-
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invention of said Claim 1, since the spacing of the
balls in the ret~; n; ng ring is arranged at a mutual
distance with ad;acent balls in the direction of
the thread pitch having their positions spaced
along the direction of thread pitch, it is possible
to have the thread pitch of the thread grooves
smaller than the diameter of the balls, the lead
angle of the thread grooves can be small, and as a
result a greater multiplication of the operating
force is obtained, and effective clamping is
obtained.
According to the invention of Claim 4 of the
invention, in addition to the effect of the
invention of said Claim 1, when the operating ring
enters the clamping state, the raised parts and the
contact parts slip against each other due to the
relative rotation between the operating ring and
the adjustment ring, generating an adjustment and
an adjustment noise, and it is possible to verify
the clamping state by this adjustment and
adjustment noise.
In another embodiment, the invention of Claim
5 of the invention is characterised by being a
clamp screw which is provided with a threaded
member with a threaded part having a female or male
thread formed on a shaft part and which screws onto
a threaded attachment part, and with a shaft-shaped
peripheral part formed on its outer surface, an
operating ring whose inner part is inserted over
the shaft-shaped peripheral part of said threaded
member and to which a rotational force is input
externally, and a flange ring fitted facing said
operating ring so as to freely rotate on said
shaft-ch~reA peripheral part of said threaded
member and permitted a slight movement in the axial
direction, and in contact with the attached object,
thread grooves of the same respective thread pitch
-
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WO 96119677 PCT/US95/16101
being engraved into the inserted and engaged inner
and outer surfaces of said threaded member and
operating ring, a plurality of balls being fitted
into said thread grooves, a restraining ring being
installed between said operating ring and flange ~=
ring with slight freedom of movement in the axial
direction with respect to the threaded member but
prevented from rotating, and a spring means being
fitted between said restraining ring and operating
ring, which r eLULIIS said operating ring to its
initial position allowing for the set number of
turns in the clamping range.
The invention of Claim 6 of the invention, in
addition to the structure of the invention of Claim
5, is characterised by being a clamp screw in which
a thrust bearing is fitted between said operating
ring and restraining ring.
The invention of Claim 7 of the invention, in
addition to the structure of the invention of Claim
5, is characterised by being a clamp screw in which
said balls, in addition to being retained by a
retaining ring fitted between the respective thread
grooves of the threaded member and the operating
ring, are arranged at a mutual distance with
adjacent balls in the direction of the thread pitch
having their positions spaced along the direction
of thread pitch.
The invention of Claim 8 of the invention, in
addition to the structure of the invention of Claim
5, is characterised by being a clamp screw in which
a thrust bearing is fitted between said operating
ring and restraining ring, an adjustment ring is
fitted between said thrust bearing and restraining
ring, raised parts being formed on one of the
circumferences of the respectively opposing
surfaces of said adjustment ring and operating
ring, contact parts which are able to slip and are
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sprung against said raised parts being formed on
the other.
With the clamp screw of Claim 5 of the
invention, when the operating ring is rotated with
the threaded part of the threaded member screwed
onto the threaded attachment part, until the flange
ring comes into contact with the object being
attached it rotates in the same way as a single
threaded member, as it forms a unit through the
assembled resistance of the structural elements.
Then when the flange ring comes in contact with the
object being attached, the rotation of the threaded
member stops and it enters the clamping state, the
rotation of the operating ring is screw fed due to
the balls moving around the thread grooves, and due
to this screw feed the movement of the operating
ring creates a pressure against the flange ring
through the restraining ring, so that this pressure
produces a clamping force on the object being
attached. Moreover, the rotation of said operating
ring during the screw feed of said operating ring
has virtually no frictional resistance due to the
movement of the balls around the thread grooves, so
that the rotative force of the operating ring can
be applied to the flange ring effectively with no
loss.
When removing the clamp screw, by rotating the
operating ring in the opposite direction to the
above, the pressure from the said operating ring on
the flange ring is released, and the clamping can
be loosened, and thereafter it can be removed like
a single threaded member. Also there is no loss of
rotative power when the operating ring is turned in
reverse, since the balls move around the thread
grooves. Furthermore, when the load is removed
from the operating ring on the flange ring side,
the operating ring returns to its initial position
_
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with respect to the threaded member due to the
spring means.
With the clamp screw of Claim 6 of the
invention, in addition to the effect of the
invention of said Claim 5, there is virtually no
frictional resistance between the operating ring
and the restraining ring, so that the rotational
force of the operating ring can be transmitted to
the flange ring effectively and without loss.
With the clamp screw of Claim 7 of the
invention, in addition to the effect of the
invention of said Claim 5, the position of the
balls is maintained by the retaining ring, ensuring
the balls have a smooth turning movement.
With the clamp screw of Claim 8 of the
invention, in addition to the effect of the
invention of Claim 5, when the operating ring
enters the clamping state, the adjustment ring also
receives the pressure between the operating ring
and stops rotating, and due to its stopping a
relative rotation takes place between the operating
ring and the adjustment ring, and adjustment and an
adjustment noise is generated by slippage between
the raised parts and the contact part, and the
clamping state can be verified by this adjustment
and adjustment noise.
According to the invention of Claim 5 of the
invention, when the flange ring comes into contact
with an attached tool, the rotation of the threaded
member stops and it enters a clamping state, the
rotation of said operating ring during screw feed
of the operating ring has virtually no frictional
resistance due to the movement of the balls around
the thread grooves, so the rotational force of the
operating ring can be transmitted effectively and
without loss to the flange ring, it is possible to
fix the clamp strongly even with a small rotational
- - -
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11
force, and manual operation can be made to exert a
sufficient clamping force.
According to the invention of Claim 6 of the
invention, in addition to the effect of the
invention of said Claim 5, since there is virtually
no frictional resistance between the operating ring
and the restraining ring during said clamping state
because of the thrust bearing, there is no loss in
rotational force in said part, and a small
operating force such as a hand movement can be made
more efficiently and effectively to have sufficient
effect as a clamping force.
According to the invention of Claim 7 of the
invention, in addition to the effect of the
invention of said Claim 5, since the spacing of the
balls in the retA;n;ng ring is arranged at a mutual
distance with adjacent balls in the direction of
the thread pitch having their positions spaced
along the direction of thread pitch, it is possible
to have the thread pitch of the thread grooves
smaller than the diameter of the balls, the lead
angle of the thread grooves can be small, and as a
result a greater multiplication of the operating
force is obtained, and effective clamping is
obtained.
According to the invention of Claim 8 of the
invention, in addition to the effect of the
invention of said Claim 5, when the operating ring
enters the clamping state, the raised parts and the
contact parts slip against each other due to the
relative rotation between the operating ring and
the adjustment ring, generating an adjustment and
an adjustment noise, and it is possible to verify
- the clamping state by this adjustment and
adjustment noise.
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12
Brief Description of the Drawinqs
Figure 1 is a cross section of the clamp
screw;
Figure 2 is an exploded diagram with parts
above the centre line in cross section;
Figure 3 is a development with part of the
ret~i n i ng ring omitted;
Figure 4 is a cross section through line A-A
in Figure 1; and
Figure 5 is a plan view of adjustment ring.
Preferred Embodiments
Preferred embodiments of the invention will
now be described based on the drawings.
The drawings show a clamp screw 10, and in
Figures 1 and 2 claim screw 10 is provided with
cylindrical threaded member 11, ring-shaped
operating ring 12, cylindrical retaining ring 14
which retains balls 13, disk-shaped adjustment ring
15, disk-shaped restraining ring 16, disk-shaped
dry metal 17, and ring-shaped flange ring 18.
At the end of said threaded member 11 is
formed a collar part 20, engagement holes 21 for a
wrench being formed in the outer surface of this
collar part 20 at an appropriate spacing. Female
thread 22 is formed on the shaft of said threaded
member 11, arc-shaped thread grooves 23 for the
movement of above-mentioned balls 13 being formed
in the circumference of the shaft on the inner side
of said collar part 20, and furthermore on its
outside surface are formed spline slots 24 which
engage with the above-mentioned restraining ring
16, and ring slots 26 which stop stopping ring 25.
Element 27 is an O-ring to provide a seal.
The above-mentioned operating ring 12 is a
ring to which rotational force is input, and is
inserted over the shaft-shaped periphery of said
threaded member 11, knurl 30 being formed on its
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13
outer surface to prevent slipping, and on its
outside surface is formed depression 31 into which
fits collar part 20 of threaded member 11 with the
above-mentioned 0-ring 27 installed, and moreover
on the inner surface are formed arc--ch~r~ thread
yLooves 32 for said balls 13 to move around and
which have the same thread pitch as said thread
y Go~es 23, and furthermore on the inside surface
is formed depression 34 which accommodates thrust
bearing 33, thrust bearing 33 thus accommodated
being in contact with the side of adjustment ring
15 mentioned above. Groove 35 is for accommodating
spring 36 to be described later. Furthermore said
thread grooves 23, 32 need not be arc-shaped but
may be the conventional triangular shape.
The above-mentioned balls 13 are retained
within retaining ring 14 so as to be able to rotate
around with a plurality of balls spaced at the
required intervals, and moreover balls 13 are
arranged at a mutual distance with adjacent balls
13, 13 in the direction of the thread pitch having
their positions spaced without clustering along the
direction of thread pitch, and by having this
structure it is arranged that the width of the
thread pitch can be formed smaller than the
diameter of balls 13. The lead angle of screw
grooves 23, 32 is set smaller than the lead angle
of female thread 22 of said threaded member 11, and
moreover it is preferable that said lead angle be
formed at an angle of 1.5 or less to avoid
loosening caused by vibration.
As shown in Figure 4, raised parts 37 are
formed on the inner surface of the inside of the
above-mentioned operating ring 12, and contact
parts 38 formed in three positions on the outer
surface of adjustment ring 15 are made to engage
with these raised parts 37. The above-mentioned
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14
contact parts 3 8 have an elasticity through being
formed via a long neck from said adjustment ring
15, and due to this elasticity contact parts 3 8 are
sprung against said raised parts 37, and when these
raised parts 3 7 and contact parts 38 rotate against
one another, in addition to obtaining adjustment of
the rotation of operating ring 12, an adjustment
noise is generated due to the engagement of contact
parts 38 in the depressions.
In housing groove 35 of the above-mentioned
operating ring 12 is a stopper 39, this stopper 39
being restrained by both ends of spring 36
accommodated in housing groove 35. In the middle
of this spring 36, as shown in Figure 5, is fitted
restrainer 40 which is formed in the above-
mentioned restraining ring 16, and sprung so that
said operating ring 12 can be returned to its
initial position when the clamping load is released
from operating ring 12.
Said restraining ring 16 has spline grooves 41
formed on its inner surface, which engage with
spline grooves 24 of above-mentioned threaded
member 11, and even with slight movement permitted
in the axial direction of said threaded member 11,
iS fitted to threaded member 11 so that rotation is
prevented.
Disk-shaped dry metal 17 has the coefficient
of friction of its surface set at the required
value, the value being adjusted up to a level where
the clamping of operating ring 12 due to the
reaction of rotating tool 42 on thread grooves 23,
32 is not excessive, and is set so that the value
ensuring slipping occurs with further rotation.
The above-mentioned flange ring 18 is fitted
to rotate at the end of spline grooves 24 of
threaded member 11 with a slight degree of movement
permitted in the axial direction, its outside
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surface applying clamping pressure against rotating
tool 42.
A male thread 44 for attachment is engraved in
the end of drive shaft 43 of the electric tool,
rotating tool 42 being fitted to this male screw 44
via an inner flange 45, and is fixed on using a
clamp screw 10 of a structure as described above.
In other words female thread 22 of threaded
member 11 is screwed onto male screw 44 of drive
shaft 43. In a state where the flange ring 18 is
not in contact with rotating tool 42, in other
words where no load is applied to said flange ring
18, it is screwed on just like a single nut,
rotating as a unit through the assembled resistance
of the structural elements of clamp screw 10.
When flange ring 18 comes into contact with
the side of rotating tool 42 and stops, the
rotation of threaded member 11 also stops
simultaneously, at which point a clamping state is
entered. In other words if operating ring 12 is
further rotated in the direction of clamping in
this state, balls 13 retained in retaining ring 14
move around thread grooves 23, 32, and operating
ring 12 is screw fed. Moreover, the movement of
these balls 13 has virtually no frictional
resistance, so the rotation of operating ring 12
can be effectively transmitted without loss of the
operating force.
The screw feed of the above-mentioned
operating ring 12 applies pressure through thrust
bearing 33 to adjustment ring 15, restraining ring
16 and dry metal 17, and furthermore exerts
pressure on flange ring 18 so that rotating tool 42
is firmly clamped.
When the above-mentioned operating ring 12
enters a clamping state, since restraining ring 16
does not rotate, when operating ring 12 rotates
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16
spring 36 is compressed in the direction of
clamping.
When operating ring 12 is clamped in the
above-described fashion, it is possible to set the
angle of rotation to approximately 90 with a
movement of the operating ring 12 that is within as
little as 0.5 mm in the axial direction.
Furthermore as the rotation of operating ring 12 is
transmitted effectively and without loss of
operating power, a strong fixed clamping can be
obt~ine~ from a small rotational force (operating
force) and sufficient clamping can be obtained from
manual operation.
Moreover there is virtually no friction with
adjustment ring 15 with respect to the rotation of
operating ring 12 due to thrust bearing 33 being
fitted, so there is no loss of this part of the
force and it can make the rotation of the operating
ring more effective.
As described above, when operating ring 12 is
rotated in the clamping state, at this point
adjustment ring 15 comes under pressure and stops,
so that a relative movement against operating ring
12 occurs, with raised parts 37 on the inside
surface of operating ring 12 riding over contact
parts 38 of adjustment ring 15 and rotating, an
adjustment and an adjustment noise being obtained
from operating ring 12 each time they ride over,
and as a result of this contact the operator is
able to confirm that a clamping state has been
achieved.
When rotating tool 42 has been fixed as
described above and this rotating tool 42 is used,
the reverse thrust caused by the resistance in use
is transmitted to flange ring 18, and this is
rotated in the direction of clamping. This reverse
rotation is transmitted to said dry metal 17 and
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17
restraining ring 16 through adjustment ring 15
until dry metal 17 slips, and a relative rotation
in the direction of clamping occurs between this
adjustment ring 15 and operating ring 12, the
mutual clamping force is increased, and due to this
increased clamping force (extra clamping) a more
effective clamping can be obtained. However, where
a reverse rotation greater than the coefficient of
friction set for dry metal 17 occurs, slipping will
occur between this dry metal 17 and flange ring 18,
so that over-clamping can be prevented.
When removing clamp screw 10 attached as
described above, operating ring 12 is rotated in
the direction of loosening. Whilst the flange ring
18 is in contact with rotating tool 42, this
rotation also causes screw feed of operating ring
12 due to balls 13 and thread grooves 23, 32.
Moreover, due to the fact that there is virtually
no frictional resistance due to the rotation of the
balls 13, this screw feed is effectively
transmitted with a small manual rotational force so
that clamping and loosening are possible.
Moreover, when the clamping of flange ring 18
is released, clamp screw lo rotates as a unit due
to the assembled resistance of the structural
elements, the rotation of operating ring 12 becomes
the rotation of threaded member 11, and female
thread 22 of said threaded member 11 can be removed
from male thread 44 of drive shaft 43.
Furthermore, when the clamping load is
released from operating ring 12, the elastic force
.of compressed spring 36 returns operating ring 12
to its initial waiting position with respect to
restraining ring 16.
In the embodiment described above, when flange
ring 18 comes into contact with rotating tool 42,
the rotation of threaded member 11 stops and it
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18
enters a clamping state, the rotation of said
operating ring 12 during screw feed of operating
ring 12 has virtually no frictional resistance due
to the movement of balls 13 around thread grooves
23, 32, so the rotational force of operating ring
12 can be transmitted effectively and without loss
to flange ring 18, it is possible to fix the clamp
strongly even with a small rotational force, and
manual operation can be made to exert a sufficient
clamping force.
Moreover, as dry metal 17 is fitted, a more
effective clamping is obtained due to the increased
clamping force (extra clamping) resulting from the
reverse rotation of rotating tool 42.
In addition, when the reverse rotation is
greater than the level at which the coefficient of
friction of dry metal 17 has been set, slippage
occurs between this dry metal 17 and the flange
ring 18, thus preventing over-clamping.
Moreover, since there is virtually no
frictional resistance between operating ring 12 and
restraining ring 16 during the above-mentioned
clamping state because of thrust bearing 33, there
is no loss of rotational force in said part, and a
small operating force such as a hand movement can
be made more efficiently and effectively to have
sufficient effect as a clamping force.
Furthermore, since the spacing of balls 13 in
retaining ring 14 is arranged at a mutual distance
with adjacent balls 13 in thread grooves 23, 32 in
the direction of the thread pitch having their
positions spaced along the direction of thread
pitch, it is possible to have the thread pitch of
thread grooves 23, 32 smaller than the diameter of
balls 13, the lead angle of thread grooves 23, 32
can be small, and as a result a greater
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19
multiplication of the operating force is obtained,
and effective clamping is obtained.
Moreover, when operating ring 12 enters the
clamping state, raised parts 37 and contact parts
38 slip against each other due to the relative
rotation between operating ring 12 and adjustment
ring 15, generating an adjustment and an adjustment
noise, and it is possible to verify the clamping
state by this adjustment and adjustment noise.
Key
10 - clamp screw
11 - threaded member
12 - operating ring
13 - ball
14 - retaining ring
15 - adjustment ring
16 - restraining ring
17 - dry metal
18 - flange ring
23, 32 - thread grooves
33 - thrust bearing
36 - spring
37 - raised parts
38 - contact parts
40 - restrainer
With respect to the correspondence of the
structure of this invention with the embodiment
described above, even where the spring means of the
invention corresponds to restrainer 40 and spring
36 of the restraining ring 16 of the embodiment,
the structure of the invention is not limited only
to the structure of the above embodiment. For
example, female thread 22 of threaded member 11 may
- be replaced with a male thread.
